U.S. patent number 7,467,042 [Application Number 11/843,801] was granted by the patent office on 2008-12-16 for method and control unit for diagnosing a valve lift adjustment system of an internal combustion engine.
This patent grant is currently assigned to Dr. Ing. h.c.F. Porsche AG. Invention is credited to Thomas Melzig, Nils Nagel, Sven Sikora.
United States Patent |
7,467,042 |
Sikora , et al. |
December 16, 2008 |
Method and control unit for diagnosing a valve lift adjustment
system of an internal combustion engine
Abstract
A method assesses the functional capability of a gas exchange
valve lift adjuster of an internal combustion engine as a function
of a measure of rotational oscillation amplitudes of a camshaft.
The measure of the rotational oscillation amplitudes is formed
repeatedly. In a situation in which the gas exchange valve lift
adjuster is to change the valve lift, it is checked whether a
change in the measure of the rotational oscillation amplitudes
occurs. The gas exchange valve lift adjuster is assessed as being
functional if a measure for the change is greater than a
predetermined threshold value. A control unit is programmed to
perform such steps.
Inventors: |
Sikora; Sven (Stuttgart,
DE), Melzig; Thomas (Leonberg-Hofingen,
DE), Nagel; Nils (Leonberg, DE) |
Assignee: |
Dr. Ing. h.c.F. Porsche AG
(Weissach, DE)
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Family
ID: |
39104375 |
Appl.
No.: |
11/843,801 |
Filed: |
August 23, 2007 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20080051972 A1 |
Feb 28, 2008 |
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Foreign Application Priority Data
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Aug 23, 2006 [DE] |
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10 2006 039 556 |
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Current U.S.
Class: |
701/114;
123/90.16 |
Current CPC
Class: |
F02D
13/0226 (20130101); Y02T 10/18 (20130101); Y02T
10/12 (20130101) |
Current International
Class: |
F02D
28/00 (20060101); F02D 3/02 (20060101); G06F
19/00 (20060101) |
Field of
Search: |
;701/114,115,101,102
;123/90.16,90.15 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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196 06 054 10 |
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Jul 1998 |
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DE |
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198 57 183 |
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Jun 2000 |
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DE |
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199 57 157 |
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Jun 2001 |
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DE |
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10316900 |
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Nov 2004 |
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DE |
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103 55 335 |
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Jun 2005 |
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DE |
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10 2004 030 992 |
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Jan 2006 |
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DE |
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WO 99/63213 |
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Dec 1999 |
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WO |
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Primary Examiner: Vo; Hieu T
Claims
The invention claimed is:
1. A method for assessing a functional capability of a gas exchange
valve lift adjuster of an internal combustion engine in dependence
on a measure of rotational oscillation amplitudes of a camshaft,
which comprises the steps of: forming the measure of the rotational
oscillation amplitudes repeatedly; checking whether a change in the
measure of the rotational oscillation amplitudes occurs if the gas
exchange valve lift adjuster changes a valve lift; and assessing
the gas exchange valve lift adjuster as being functional if a
measure for a change is greater than a predetermined threshold
value.
2. The method according to claim 1, wherein if the gas exchange
valve lift adjuster has been assessed as being functional, storing
the measure of the rotational oscillation amplitudes used for the
assessing in a non-volatile memory.
3. The method according to claim 1, which further comprises:
forming a first measure of the rotational oscillation amplitudes
after a setting of a first value of the valve lift; and forming a
second measure of the rotational oscillation amplitudes after a
setting of a second value of the valve lift.
4. The method according to claim 1, which further comprises
performing the checking step after the valve lift is set to a
smaller valve lift setting.
5. The method according to claim 3, which further comprises setting
the first value of the valve lift at idle after a cold start of the
internal combustion engine.
6. The method according to claim 3, which further comprises setting
the second value of the valve lift at idle when the internal
combustion engine is warm.
7. The method according to claim 3, which further comprises:
setting the first value of the valve lift in a case of a
comparatively high torque or power demand on the internal
combustion engine; and setting the second value of the valve lift
in a case of a comparatively low torque or power demand on the
internal combustion engine.
8. The method according to claim 3, which further comprises:
forming the first measure in an n-th driving cycle; and forming the
second measure in an (n-1)-th driving cycle.
9. The method according to claim 1, wherein, before a check, which
is carried out for a first time in a certain driving cycle, as to
whether an attempt is reflected in a change in the measure of the
rotational oscillation amplitudes, performing the following steps:
checking whether a second measure of the rotational oscillation
amplitudes can be read out of a non-volatile memory; and carrying
out the check with a newly-formed first measure and the second
measure which is read out from the memory.
10. The method according to claim 1, which further comprises
assessing the gas exchange valve lift adjuster as being functional
if the measure for the change is greater than a predetermined
threshold value.
11. The method according to claim 1, wherein if the gas exchange
valve lift adjuster is assessed as being non-functional, storing
prevailing ambient conditions together with a fault message at a
time at which a fault occurred.
12. The method according to claim 3, wherein in an event of a fault
message based on a comparison of the first and second measures
formed in a driving cycle, storing prevailing ambient conditions at
a time at which the first measure was formed.
13. A control system for assessing a functional capability of a gas
exchange valve lift adjuster of an internal combustion engine in
dependence on a measure of rotational oscillation amplitudes of a
camshaft, the control system comprising: a control unit programmed
to: repeatedly form the measure of the rotational oscillation
amplitudes; check whether a change in the measure of the rotational
oscillation amplitudes occurs if the gas exchange valve lift
adjuster changes a valve lift; and assess the gas exchange valve
lift adjuster as being functional if a measure for the change is
greater than a predetermined threshold value.
14. The control system according to claim 13, wherein said control
unit is programmed to store the measure of the rotational
oscillation amplitudes in a non-volatile memory if the gas exchange
valve lift adjuster has been assessed as being functional.
15. The control system according to claim 13, wherein said control
unit is programmed to: form a first measure of the rotational
oscillation amplitudes after a setting of a first value of the
valve lift; and form a second measure of the rotational oscillation
amplitudes after a setting of a second value of the valve lift.
16. The control system according to claim 13, wherein said control
unit is programmed to perform the checking step after the valve
lift is set to a smaller valve lift setting.
17. The control system according to claim 15, wherein said control
unit is programmed to set the first value of the valve lift at idle
after a cold start of the internal combustion engine.
18. The control system according to claim 15, wherein said control
unit is programmed to set the second value of the valve lift at
idle when the internal combustion engine is warm.
19. The control system according to claim 15, wherein said control
unit is programmed to: set the first value of the valve lift in a
case of a comparatively high torque or power demand on the internal
combustion engine: and set the second value of the valve lift in a
case of a comparatively low torque or power demand on the internal
combustion engine.
20. The control system according to claim 15, wherein said control
unit is programmed to: form the first measure in an n-th driving
cycle; and form the second measure in an (n-1)-th driving
cycle.
21. The control system according to claim 13, wherein said control
unit is programmed to perform the following steps before a check,
which is carried out for a first time in a certain driving cycle,
as to whether an attempt is reflected in a change in the measure of
the rotational oscillation amplitudes: check whether a second
measure of the rotational oscillation amplitudes can be read out of
a non-volatile memory; and carry out the check with a newly-formed
first measure and the second measure which is read out from the
memory.
22. The control system according to claim 13, wherein said control
unit is programmed to assess the gas exchange valve lift adjuster
as being functional if the measure for the change is greater than
the predetermined threshold value.
23. The control system according to claim 13, wherein said control
unit is programmed to store prevailing ambient conditions together
with a fault message at a time at which a fault occurred if the gas
exchange valve lift adjuster is assessed as being
non-functional.
24. The control system according to claim 15, wherein said control
unit is programmed to store prevailing ambient conditions at a time
at which the first measure was formed in an event of a fault
message based on a comparison of the first and second measures
formed in a driving cycle.
Description
CROSS-REFERENCE TO RELATED APPLICATION
This application claims the priority, under 35 U.S.C. .sctn. 119,
of German application DE 10 2006 039 556.5, filed Aug. 23, 2006;
the prior application is herewith incorporated by reference in its
entirety.
BACKGROUND OF THE INVENTION
Field of the Invention
The invention relates to a method for assessing the functional
capability of a gas exchange valve lift adjuster of an internal
combustion engine in dependence on a measure of rotational
oscillation amplitudes of a camshaft and to a control unit which is
set up for assessing the functional capability of a gas exchange
valve lift adjuster of the internal combustion engine in dependence
on the measure of the rotational oscillation amplitudes of the
camshaft.
A method of the type and a control unit of the type are in each
case known from published, non-prosecuted German patent application
DE 199 57 157 A1, corresponding to U.S. Pat. No. 6,357,404. Details
regarding a mechanical implementation of a lift, which can be
switched between a minimum and a maximum value, of a gas exchange
valve can for example be found in German patent DE 196 06 054 C2
(see in particular FIG. 2 in the document).
The applicant also offers motor vehicles having a system for
adjusting the angular position of intake camshafts and for
switching the valve lift of the intake valves. This so-called
"Variocam Plus" system primarily permits high power and torque
values in addition to the best possible running quality, favorable
fuel consumption and low pollutant emissions.
The valve lift adjusting system is composed of switchable bucket
tappets which are controlled by an electrohydraulic switching
valve. The bucket tappets are composed of two tappets which bear
one inside the other and can be locked by a pin. Here, selectively
the inner tappet acts on the intake valves via a small cam of the
camshaft, or the outer tappet acts on the intake valves via a large
cam of the camshaft. The small cam generates the small lift and the
large cam generates the large lift. The variation of the intake
control times is carried out in a stepless fashion by a camshaft
adjuster which is attached at the end side of the camshaft and
which operates on the vane principle. The actuation takes place by
use of an electrohydraulic control valve.
In order for example to optimize the gas intake during the
warm-running phase at low temperatures, large valve lifts with late
control times are set then. Operation with a large valve lift
shortly after the start of a cold internal combustion engine
additionally has a favorable effect on the exhaust gas emissions,
and is therefore utilized as part of a cold start emission
reduction strategy (CSERS).
In the case of a warm internal combustion engine, in the middle
rotational speed and low load range, small valve lifts with early
control times are set in order to reduce the fuel consumption and
the exhaust gas emissions. High torques and maximum power are
obtained by setting larger valve lifts and earlier control
times.
Under the demands of the California Air Resources Board (CARB),
faults of systems which are used within the context of a CSERS must
be detected by on-board diagnosis. It is additionally demanded that
a gas exchange valve lift adjuster is detected as being faulty if,
in internal combustion engines with a plurality of groups or banks
of cylinders, all of the groups operate with an incorrect valve
lift. In published, non-prosecuted German patent application DE 199
57 157 A1, as cited in the introduction, rotational oscillations of
two cylinder groups are compared with one another. In the event of
deviations, a functional signal is generated, which signalizes a
fault. Such deviations occur if two cylinder banks operate with
different valve lifts, but not if all of the cylinder banks operate
with an incorrect valve lift.
SUMMARY OF THE INVENTION
It is accordingly an object of the invention to provide a method
and a control unit for diagnosing a valve lift adjustment system of
an internal combustion engine which overcomes the above-mentioned
disadvantages of the prior art devices and methods of this general
type, which permit reliable detection of faults in a valve lift
adjusting system, in the case of which all of the groups of
cylinders operate with an incorrect valve lift and have an effect
on a CSERS.
With the foregoing and other objects in view there is provided, in
accordance with the invention, a method for assessing a functional
capability of a gas exchange valve lift adjuster of an internal
combustion engine in dependence on a measure of rotational
oscillation amplitudes of a camshaft. The method includes the steps
of forming the measure of the rotational oscillation amplitudes
repeatedly; checking whether a change in the measure of the
rotational oscillation amplitudes occurs if the gas exchange valve
lift adjuster changes a valve lift; and assessing the gas exchange
valve lift adjuster as being functional if a measure for a change
is greater than a predetermined threshold value.
By the invention, it is checked whether a change, which is to be
expected, of the valve lift is reflected in the rotational
oscillation amplitudes. Here, the rotational oscillation amplitudes
can be measured using a camshaft sensor which is present in any
case for the closed-loop control and diagnosis of the angular
position of an intake camshaft. For the diagnosis, changes of the
valve lift in normal operation of the internal combustion can be
utilized so that the check does not require any interruption to the
operation of the internal combustion engine, and can be carried out
without additional sensors.
In accordance with an added mode of the invention, if the gas
exchange valve lift adjuster has been assessed as being functional,
the measure of the rotational oscillation amplitudes used for the
assessing is stored in a non-volatile memory.
In accordance with an addition mode of the invention, a first
measure of the rotational oscillation amplitudes is formed after a
setting of a first value of the valve lift; and a second measure of
the rotational oscillation amplitudes is formed after a setting of
a second value of the valve lift.
In accordance with another mode of the invention, the checking step
after the valve lift is set to a smaller valve lift setting is
performed.
In accordance with a further mode of the invention, the first value
of the valve lift is set at idle after a cold start of the internal
combustion engine. The second value of the valve lift is set at
idle when the internal combustion engine is warm.
In accordance with yet another mode of the invention, the first
value of the valve lift is set in a case of a comparatively high
torque or power demand on the internal combustion engine; and the
second value of the valve lift is set in a case of a comparatively
low torque or power demand on the internal combustion engine.
In accordance with yet a further mode of the invention, the first
measure is formed in an n-th driving cycle, and the second measure
is formed in an (n-1)-th driving cycle.
Before a check, which is carried out for a first time in a certain
driving cycle, as to whether an attempt is reflected in a change in
the measure of the rotational oscillation amplitudes, the following
steps are performed: checking whether a second measure of the
rotational oscillation amplitudes can be read out of a non-volatile
memory; and carrying out the check with a newly-formed first
measure and the second measure which is read out from the
memory.
In accordance with another mode of the invention, the gas exchange
valve lift adjuster is assessed as being functional if the measure
for the change is greater than a predetermined threshold value. If
the gas exchange valve lift adjuster is assessed as being
non-functional, prevailing ambient conditions together with a fault
message are store a time at which a fault occurred.
In accordance with a concomitant mode of the invention, in an event
of a fault message based on a comparison of the first and second
measures being formed in a driving cycle, prevailing ambient
conditions at a time at which the first measure was formed are
stored.
With the foregoing and other objects in view there is provided, in
accordance with the invention, a control system for assessing a
functional capability of a gas exchange valve lift adjuster of an
internal combustion engine in dependence on a measure of rotational
oscillation amplitudes of a camshaft. The control system contains a
control unit programmed to: repeatedly form the measure of the
rotational oscillation amplitudes; check whether a change in the
measure of the rotational oscillation amplitudes occurs if the gas
exchange valve lift adjuster changes a valve lift; and assess the
gas exchange valve lift adjuster as being functional if a measure
for the change is greater than a predetermined threshold value.
Ideally the control unit is programmed to carry out the method in
the various modes recited above.
Other features which are considered as characteristic for the
invention are set forth in the appended claims.
Although the invention is illustrated and described herein as
embodied in a method and a control unit for diagnosing a valve lift
adjustment system of an internal combustion engine, it is
nevertheless not intended to be limited to the details shown, since
various modifications and structural changes may be made therein
without departing from the spirit of the invention and within the
scope and range of equivalents of the claims.
The construction and method of operation of the invention, however,
together with additional objects and advantages thereof will be
best understood from the following description of specific
embodiments when read in connection with the accompanying
drawings.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING
FIG. 1 is an illustration showing the technical field of the
invention;
FIGS. 2A and 2B are illustrations showing a known technical
implementation of valve lift switching;
FIG. 3 is a graph showing corresponding profiles of the valve lift
over the crankshaft rotational angle;
FIG. 4 is a functional block diagram showing a routine which is
processed in the control unit during the evaluation of a signal of
a camshaft sensor;
FIG. 5 is a graph showing a profile of a diagnosis variable over
time for time sections with a large valve lift and with a small
valve lift;
FIG. 6 is a flow chart showing a first exemplary embodiment of a
method according to the invention;
FIG. 7 is a flow chart showing a second exemplary embodiment of a
method according to the invention; and
FIG. 8 is a flow chart showing a third exemplary embodiment of a
method according to the invention.
DETAILED DESCRIPTION OF THE INVENTION
Referring now to the figures of the drawing in detail and first,
particularly, to FIG. 1 thereof, there is shown an internal
combustion engine 10 which has at least one combustion
chamber/cylinder 12. An air/fuel mixture which flows into the
combustion chamber 12 via an intake system 14 is ignited by a spark
plug 16. After the combustion, resulting residual gases are
discharged via an exhaust system 18. The filling and emptying of
the combustion chamber 12, which is also referred to as a gas
exchange, is controlled by at least one intake valve 20 and at
least one exhaust valve 22 which are actuated by associated
camshafts 24 and 26. Disposed between the intake valve 20 and the
associated camshaft 24 is a valve lift adjusting system 28 which is
activated by a control unit 30 with a signal B_vs. A valve lift
adjusting system 31 can also be disposed between the exhaust valve
22 and its associated camshaft 26.
In order to control the valve lift and further functions of the
internal combustion engine 10, the control unit 30 processes
signals of various sensors which are not listed here in their
entirety below: an air mass sensor 32 measures a mass mL of the air
flowing into combustion chambers 12 of the internal combustion
engine 10, which air is controlled by a throttle flap 34 and by the
control unit 30 with a signal DK which determines the opening angle
of the throttle flap 34. The opening angle DK of the throttle flap
34 is therefore known in the control unit 30 or is signaled to the
control unit 30 if appropriate by a non-illustrated throttle flap
sensor. A crankshaft sensor 36 measures an angular position
.degree. CA and the rotational speed n of a crankshaft 38 of the
internal combustion engine 10. Similarly, a camshaft sensor 40
measures the angular position .degree. NW of at least one of the
two camshafts 24, 26. A driver demand transducer 42 transmits a
torque demand to the control unit 30, and at least one exhaust gas
probe 44 which is disposed in the exhaust system 18 of the internal
combustion engine 10 delivers an item of information regarding the
concentration of an exhaust gas constituent, preferably oxygen, to
the control unit 30.
The control unit 30 is set up, in particular programmed, to carry
out or control the process of at least one of the methods proposed
here. Here, if a fault is detected, then, if appropriate after
statistical validation, the fault is indicated by a fault lamp 50
which is activated by the control unit 30.
FIGS. 2A and 2B schematically show a known technical implementation
of valve lift switching for the intake valve 20. The mechanism of
the valve lift adjusting system 28, also referred to in the
following as the valve lift adjuster 28, has two concentric bucket
tappets 52, 54 which can be decoupled from one another (FIG. 2A) or
coupled to one another (FIG. 2B) by the signal B_vs from FIG. 1.
The camshaft 24 has cam regions 56, 58 of different eccentricity,
with the outer cam regions 56 having a larger eccentricity and
interacting with the outer bucket tappet 52. Here, the intake valve
20 is actuated by the inner bucket tappet 54.
In the case of FIG. 2A, the two concentric bucket tappets 52 and 54
are not coupled to one another, so that the inner bucket tappet 54
interacts with the region 58 of smaller eccentricity of the
camshaft 24, which leads as a result to a comparatively small valve
lift h_min. In this switching state of the valve lift adjuster 28,
the relatively large movement of the outer bucket tappet 52 is not
transmitted to the intake valve 20.
In the case of FIG. 2B, in contrast, the two bucket tappets 52 and
54 are coupled to one another, which at the same time leads to a
decoupling of the inner bucket tappet 54 from its associated cam
region 58. In this case, the relatively large eccentricity of the
cam regions 56 is transmitted via the outer bucket tappets 52 and
the inner bucket tappet 54 which is coupled thereto to the intake
valve 20, resulting in a comparatively large valve lift h_max. FIG.
3 shows resulting valve lift curves 60, 62 over the angular
position .degree. CA of the crankshaft 38.
FIG. 4 shows a functional block diagram of a routine which is
processed in the control unit 30 during the evaluation of the
signal .degree. NW of the camshaft sensor 40. A routine of the type
is carried out in any case, for the diagnosis of the camshaft
adjuster, in variable valve controllers which also influence the
phase shift between the camshafts 24 and 26 and/or the crankshaft
by a camshaft adjustment. The rotation of a transducer wheel which
is connected to the camshaft is reflected in the signal of the
camshaft angle sensor 40. The camshaft angle sensor 40 therefore
delivers a signal whose flanks correlate with angular positions of
the camshaft. Four flanks f typically occur per camshaft
rotation.
The block 64 counts the flanks f and the block 66 determines the
angle alpha (f) of the present flank (f). The angle determination
takes place in one embodiment by comparing flanks in the signal of
the camshaft sensor with flanks in the signal of the crankshaft
sensor 36. In a comparison timespan, the crankshaft sensor 36
delivers more flanks than the camshaft sensor 40. The spacing
between two flanks of the signal of the camshaft sensor 40 can
therefore be determined by the number of flanks of the signal of
the crankshaft sensor 36 which are counted between the flanks. By
counting time sections between two flanks of the crankshaft sensor,
the angle resolution can be increased yet further.
The actual value, which is formed in this way or in some other way,
of the angle alpha (f) of a flank f in the signal of the camshaft
sensor 40 is compared in the block 68 with a nominal value
alpha_nom (f) of the angle alpha (f). The comparison takes place in
one embodiment by forming the difference D of the nominal value
alpha_nom (f) and the actual value alpha (f). The difference D is
provided by block 70 as a diagnosis variable and, within the
context of an embodiment as a measure for rotational oscillation
amplitudes, is also used for the diagnosis of the valve lift
adjuster.
FIG. 5 shows the profile of the difference D or diagnosis variable
D over the time t for a first time section dt_1 in which a large
valve lift is set, and for a second, later time section dt_2 in
which a small valve lift is set. It can be clearly seen that an
oscillation, more precisely a rotational oscillation, whose
rotational oscillation amplitude is approximately twice as large in
the case of the large valve lift than in the case of the relatively
small valve lift, is superposed on the mean value of the
difference, which corresponds to a mean deviation of the angular
position from a nominal value. The cause for the different
rotational oscillation forms lies ultimately in that, during
operation with a relatively large valve lift, greater elastic
restoring forces from the valve actuating mechanism retroact on the
camshaft.
FIG. 6 shows a first embodiment (diagnosis strategy I) of a method
according to the invention, as is carried out by the control unit
30 from FIG. 1. Here, in a step 72 which is reached from a
superordinate main program MP in the step 70 for controlling the
internal combustion engine 10, it is checked whether certain
operating conditions B are met. An example of such a condition is
that the internal combustion engine 10 is running at idle. When the
operating condition is met, a step 74 follows in which the control
unit 30, in one embodiment, checks whether or not the internal
combustion engine 10 should presently be operated with a large
valve lift VH. The internal combustion engine 10 should be operated
with a large valve lift VH for example when the above-described
conditions for a CSERS are present. If this is the case, it is
checked in step 76 whether a first measure M1 of the rotational
oscillation amplitudes has already been formed while the internal
combustion engine 10 is cold. During the first run-through of the
described sequence of steps after a start, this is not yet the
case, so that the method follows a step 78 in which the first
measure M1 is formed while the internal combustion engine 10 is
cold. The first measure M1 is thus formed in particular while a
CSERS is being carried out. The first measure M1 is set at idle in
particular after a cold start of the internal combustion engine,
with a large valve lift as the first value of the valve lift.
As has already been mentioned, in the case of a functional valve
lift adjusting system, a large valve lift VH should be set during
the CSERS. The first measure M1 is, in one embodiment, formed by
the following sequence of steps: formation of a sliding mean value
of the difference or diagnosis value illustrated in FIG. 5,
formation of the magnitude of the deviation of the diagnosis
variable from the sliding mean value, integration of the magnitude,
and normalization of the integration result to the integration
time.
The greater the value obtained for M1, the larger the rotational
oscillation amplitude and therefore the amplitude of the
oscillation of the diagnosis variable D from FIG. 5 is. In an
alternative embodiment, the first measure M1 is formed by the
following sequence of steps: formation of a sliding mean value of
the difference or diagnosis value illustrated in FIG. 5, formation
of the magnitude of the deviation of the diagnosis variable from
the sliding mean value, and accumulation of the magnitude.
A further alternative embodiment provides the formation of the
first measure M1 by the following steps: determining the minimum
and the maximum of the difference or diagnosis variable during one
camshaft rotation, forming the difference between the minimum and
maximum, and accumulation of the difference.
In step 80, the first measure M1 is stored, and the method returns
to step 72. As long as the CSERS function is to be active, a
sequence of steps 72, 74, 76 will then be run through repeatedly
since the query in step 76 is affirmed after the first formation of
the variable M1.
If the CSERS function is then no longer to be active, for example
because a predefined timespan has expired after a cold start of the
internal combustion engine 10, the step 74 is followed by a step 82
in which it is checked again whether a first measure M1 is present.
If this is not the case, the diagnosis is ended by a branch to step
83.
If, in contrast, a measure M1 has already been formed in the
present driving cycle, there follows a step 84 in which a second
measure M2 for the rotational oscillation amplitudes is formed. As
has already been mentioned, a small valve lift VH should be set
outside the CSERS at idle. When the internal combustion engine is
warm, at idle, the smaller, second value of the valve lift is
set.
Overall, therefore, a setting of a first value of the valve lift is
required first, during an active CSERS. When the first value is
required, a first measure of the rotational oscillation amplitudes
is formed. When the CSERS is ended, a setting of a second value of
the valve lift is required, and when the second value is required,
a second measure of the rotational oscillation amplitudes is
formed.
The second value of the valve lift is preferably smaller than the
first value of the valve lift, when the check after a cold start
takes place. The reason for this is that a large valve lift is
initially set after a cold start in any case. The utilization of
this predefined sequence during the diagnosis therefore permits an
early diagnosis without interrupting the operation of the internal
combustion engine.
The formation of the second measure M2 preferably takes place in
the same way as the formation of the first measure M1, that is to
say by normalizing an integral of deviations of the rotational
oscillation amplitudes from their mean value, or by one of the two
other alternatives specified further above. This ensures the
comparability of the measures M1 and M2. The second measure M2 is
stored in step 86.
A comparison of the first measure M1 with the second measure M2
then takes place in step 88. For this purpose, in one embodiment of
the step 88, the difference M1-M2 or the quotient M1/M2 is formed
as a comparison result, and in step 90, it is checked whether the
comparison result meets a fault criterion. As FIG. 5 shows,
different rotational oscillation amplitudes and therefore different
measures M1, M2 can be expected when the valve lift adjusting
system is functional. If the formed values for M1, M2 are too
similar, this is evaluated in step 92 as a fault.
As a criterion for the similarity, in the case of the difference
M1-M2, the magnitude of the difference M1-M2 can be compared with a
threshold value. In the case of the quotient M1/M2, the deviation
of the quotient from the value 1 can be compared with a threshold
value. In both cases, a fault manifests itself in that the
threshold value is not exceeded. The program then branches to step
92 in which a fault is evaluated. If, in contrast, the threshold
value is exceeded, or more generally, if the fault criterion in
step 90 is not met, the valve lift adjusting system is evaluated in
step 94 as being functional (OK).
FIG. 7 shows a second embodiment (diagnosis strategy II) of a
method according to the invention, as is carried out by the control
unit 30 from FIG. 1. Here, steps 70 to 94 are carried out, as have
already been explained in connection with the diagnosis strategy I
from FIG. 6. For understanding of the steps 70 to 94, reference is
therefore made to the corresponding explanations with regard to the
diagnosis strategy I.
For clarification of the differences between the diagnosis
strategies I and II, it is to be noted that the diagnosis strategy
I detects a fault only once the two measures M1 and M2 have been
determined within a driving cycle. As a result, the diagnosis
strategy I provides a measurement and evaluation of the diagnosis
variable at idle after a cold start. At this time, the engine
should be operated with a large valve lift. The result of the
evaluation is stored as a first measure M1. At a later time, when
the internal combustion engine 10 is to be operated with a
relatively small valve lift, the diagnosis variable should again be
measured at idle and evaluated in the "warm" evaluation window
(steps 84 and 86 in FIG. 6). The result of the second evaluation is
stored as a second diagnosis variable M2. At the time of the
determination of the second measure M2, the CSERS function is thus
already concluded.
The diagnosis strategy II of FIG. 7, in contrast, permits fault
detection during an active CSERS. This is obtained in that, after
the formation of the first measure M1 in a present driving cycle, a
second measure M2 from a previous driving cycle is used. For this
purpose, the embodiment of FIG. 7 provides that, after the step 80
in which the first measure M1 is stored, it is initially queried by
a step 81 whether a second measure M2_old from a previous driving
cycle is present. If the query is affirmed, the program branches to
the already-described step 88 in which the first measure M1 is
compared with the second measure M2, in this case the second
measure M2_old. If, in contrast, no second measure M2_old from a
previous driving cycle is available, the query in step 81 is
negated and a return is then made to step 72 as has already been
described in connection with FIG. 6. An embodiment of the diagnosis
strategy II is therefore characterized in that the first measure is
formed in an n-th driving cycle, and the second measure is formed
in an (n-1)-th driving cycle.
Here, in the context of the diagnosis strategy II, before a check,
which is carried out for the first time in a certain driving cycle,
as to whether an attempt to change the valve lift is reflected in a
change in the measure for rotational oscillation amplitudes, it is
initially checked whether a second measure of the rotational
oscillation amplitudes can be read out of the non-volatile memory.
If this is the case, the check is carried out with the newly-formed
first measure and the second measure which is read out from the
memory.
In order to be able to carry out the diagnosis strategy II, after
each OK evaluation of the system, the present second measure M2 is
written as M2_old into a non-volatile memory of the control unit
30, so that this can be queried in a following driving cycle. The
storage thus takes place in particular when the gas exchange valve
lift adjuster is assessed as being functional.
As has already been mentioned further above, the internal
combustion engine 10 is operated with a large valve lift not only
in the context of a CSERS function. Large valve lifts are also set
when the internal combustion engine 10 is warm in order to obtain
high torque values and, at a simultaneously high rotational speed,
high power values. In the range of medium rotational speeds and low
torque demand, in contrast, in the case of a functional valve lift
adjusting system, small valve lifts are set in order to reduce the
fuel consumption and the exhaust gas emissions.
In a third embodiment, also referred to as a diagnosis strategy
III, a measure for the rotational oscillation amplitudes in
operating states with a large valve lift VH_large and with a small
valve lift VH_small is measured and evaluated if predetermined
operating conditions are met. Depending on the operating state, the
formed measure is stored as M_VH_large for the large valve lift
VH_large or as a measure M_VH_small for the small valve lift
VH_small. Here, the large value VH_large is set in the event of a
comparatively high torque or power demand on the internal
combustion engine, and the second, relatively small value VH_small
is set in the event of a comparatively low torque or power demand
on the internal combustion engine.
After the evaluation of one operating state is complete, the
evaluation of the in each case other operating state is awaited. If
this has also taken place, both results are evaluated for fault
detection.
FIG. 8 shows a flow diagram of such an embodiment. For this
purpose, in a step 100 which is reached from a superordinate main
program MP, which expires in step 70, for controlling the internal
combustion engine 10, it is checked whether a large valve lift
VH_large is to be presently set. If this query is affirmed, there
follows a step 102 in which it is checked whether predetermined
operating conditions B_large are met, which permit an evaluation of
rotational oscillation amplitudes at a large valve lift VH_large.
If this query is also affirmed, there follows a step 104 in which
it is checked whether a measure M_VH_large is already present.
During the first run-through of the sequence of steps, this is
generally not the case, so that the method branches to the step 106
in which a measure M_VH_large is formed.
The measure M_VH_large is formed here by one of the embodiments as
have been explained further above with the formation of the
measures M1 and M2. The result is stored as the measure M_VH_large
in step 108. In the following step 110, it is checked whether a
measure M_VH_small is already present, which will not be the case
during the first run-through of the method. The program
correspondingly branches back to step 100. As long as the large
valve lift VH_large is to remain set, the sequence of steps 100,
102 and 104 will be run through repeatedly since the query in step
104 is affirmed after the first storing of the measure
M_VH_large.
If a relatively small valve lift VH_small is then demanded at some
time, the query in step 100 is negated and there follows a step 112
in which it is checked whether operating conditions B_small for the
formation of a measure M_VH_small for rotational oscillation
amplitudes at a small valve lift VH_small are met. An affirmation
of the query leads to the step 124 which checks whether a measure
M_VH_small is present. If this is not the case, there follows in
step 126 a formation of the measure M_VH_small for the amplitude of
the rotational oscillations at a small valve lift, and a storage of
the measure in step 128.
The step 130 then serves to check whether a measure M_VH_large is
present. If the query is affirmed, the program branches to the
sequence of steps from steps 88 to 94, which have already been
explained and in which M_VH_large and M_VH_small are compared with
one another in order to assess the valve lift adjusting system as
being functional (system OK) or, in step 92, as faulty.
Each of the three diagnosis strategies I, II and III therefore
constitutes an exemplary embodiment of a method for assessing the
functionality of a gas exchange valve lift adjuster of an internal
combustion engine as a function of a measure for rotational
oscillation amplitudes of a camshaft, in which method the measure
for the rotational oscillation amplitudes is formed repeatedly, in
which method, in a situation in which the gas exchange valve lift
adjuster is to change the valve lift, it is checked whether a
change in the measure of the rotational oscillation amplitudes
occurs, and in which method the gas exchange valve lift adjuster is
assessed as being functional if a measure for the change is greater
than a predetermined threshold value. In one preferred embodiment,
the prevailing ambient conditions are stored at the time at which a
fault occurs. An ensemble of such ambient conditions is also
referred to below as a freeze frame. Such ambient conditions are
for example values of the rotational speed, a temperature T, a
driver demand or other operating parameters of the internal
combustion engine 10. If the measure M2_old is provided for fault
detection (diagnosis strategy II), a freeze frame is always stored
in the event of a fault being detected.
If the second measure M2_old is not provided for fault detection
(diagnosis strategy I), valve lift faults which occur when a CSERS
is active can in principle be detected only during the later
formation of the measure M2 after the warm-running phase. Since the
fault is generally present in the cold state, the prevailing
ambient conditions at the time at which the fault is detected no
longer correlate with the ambient conditions which prevailed when
the fault occurred in the cold state. For this reason, M2_old is
used in order to set a fault suspicion after the formation of the
first measure M1 when the internal combustion engine is cold.
A fault suspicion is set if the difference between the first
measure M1 and the second measure M2_old is less than a
predetermined threshold value. A freeze frame is immediately stored
in the event of a fault suspicion. If no fault suspicion is
present, then in the same driving cycle, a freeze frame is stored
in the case of a later fault detection after the "warm" evaluation
window. Always only one freeze frame is therefore stored during a
journey, either in the event of a fault suspicion, or in the event
of a fault being detected.
* * * * *